EP1136724B1 - Transmission continue du type torique pour véhicules - Google Patents

Transmission continue du type torique pour véhicules Download PDF

Info

Publication number
EP1136724B1
EP1136724B1 EP01106700A EP01106700A EP1136724B1 EP 1136724 B1 EP1136724 B1 EP 1136724B1 EP 01106700 A EP01106700 A EP 01106700A EP 01106700 A EP01106700 A EP 01106700A EP 1136724 B1 EP1136724 B1 EP 1136724B1
Authority
EP
European Patent Office
Prior art keywords
traction
oil
root
ratio
continuously variable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01106700A
Other languages
German (de)
English (en)
Other versions
EP1136724A3 (fr
EP1136724A2 (fr
Inventor
Kenshi Ushijima
Toshikazu Nanbu
Nobutaka Chiba
Jun Watanabe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Publication of EP1136724A2 publication Critical patent/EP1136724A2/fr
Publication of EP1136724A3 publication Critical patent/EP1136724A3/fr
Application granted granted Critical
Publication of EP1136724B1 publication Critical patent/EP1136724B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
    • F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
    • F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0487—Friction gearings
    • F16H57/049—Friction gearings of the toroid type

Definitions

  • the present invention relates to a toroidal-type continuously variable transmission (CVT) for automobiles, which is used to continuously control change gear ratio, and more specifically to a surface roughness structure of rolling elements of the toroidal-type CVT, such as an input disk, an output disk and a power roller, as disclosed in DE 19 829 631 A and corresponding to the preamble of claims 1, 4, 9 and 12.
  • CVT continuously variable transmission
  • United States Patent Serial No. 5,676,618 discloses one example of the toroidal-type CVT, which is incorporated herein by reference.
  • Fig. 1 shows the basic structure of the toroidal-type CVT.
  • the toroidal-type CVT includes a plurality of metal rolling elements contacting one another through a traction oil film.
  • the rolling elements include input disk 3 connected with input shaft 1, output disk 5 connected with output shaft 2, and power rollers 6, 6 interposed between input disk 3 and output disk 5 and rotatable to transmit rotational force from input disk 3 to output disk 5.
  • Each power roller 6 has a tiltable roller shaft such that power roller 6 is inclined relative to input and output disks 3 and 5 when the roller shaft tilts.
  • Power roller 6 is contacted with input disk 3 and output disk 5 through a traction oil. When power roller 6 is inclined, the contact between power roller 6 and input and output disks 3 and 5 shifts. This changes the ratio of the torque radius of input disk 3 to that of output disk 5 to thereby continuously change the transmission ratio.
  • Table 1 shows one example of the results of measurement of a surface structure or texture, specifically, a surface roughness, of the mutually contact surfaces of input and output disks 3 and 5 and power roller 6 of the toroidal-type CVT, which surfaces are hereinafter referred to as traction surfaces.
  • Surface structure Measurement results Ra JIS B0601 0.018 ⁇ m Rq 0.022 ⁇ m Mr2 (DIN4776) 86.67 % Rk (DIN4776) 0.055 ⁇ m Rvk (DIN4776) 0.027 ⁇ m Vo 1.8x10 -6 mm 3 /mm 2 K 0.54
  • the traction surfaces of the rolling elements of the toroidal-type CVT in the earlier technique have the surface structure in which arithmetical mean roughness Ra prescribed by JIS B0601-1994 is not more than 0.05 ⁇ m, root-mean-square roughness Rq is not more than 0.07 ⁇ m, oil retention volume Vo is not more than 1.3x10 -5 mm 3 /mm 2 , and oil retention depth ratio K is less than 0.9.
  • the traction surfaces are subjected to grinding and super-finishing such that the surface roughness is limited to a sufficiently small level in height, that is, arithmetical mean roughness Ra of not more than 0.05 ⁇ m.
  • arithmetical mean roughness Ra means the mean deviation obtained by dividing the area defined by the roughness curve f(x) and the mean line, i.e., X-axis, as shown in Fig. 2A, by the reference length L.
  • root-mean-square roughness Rq means the square root of the mean deviation obtained by dividing the area defined by the mean line (X-axis) and the curve obtained by squaring the distance between the roughness curve f(x) and the mean line (X-axis), as shown in Fig. 2B, by the reference length L.
  • DIN4776 defines parameters Mr1, Mr2, Rpk, Rvk and Rk for evaluation of lubricating characteristic of a surface structure, based on an initial wear part, a substantial contact part, and an oil retention part, which are separated from a bearing curve (material ratio curve). Parameters Mr1, Mr2, Rpk, Rvk and Rk are determined as follows.
  • Rk Height difference between intersections c and d is represented by Rk ( ⁇ m).
  • Rk indicates a height of long-period wear which is reduced by wear during a long period until the surface is worn out to unuseable state.
  • Vo indicates a volume of oil retained in oil retention depth Rvk per 1 mm 2 (see Fig. 4).
  • the ratio of the transmission force to the pressing force is traction coefficient. Accordingly, if the traction coefficient is small, a large pressing force will be required to be applied to the rolling elements for obtaining a predetermined transmission force. Then, respective components will be increased in weight in order to assure the strength of the components against the large pressing force. Further, friction loss of bearings supporting the components will increase, leading to loss of automobile power. There is a demand for eliminating such undesired possibilities in the CVT in the earlier technique.
  • An object of the present invention is to provide a toroidal-type continuously variable transmission (CVT) for automobiles which includes rolling elements capable of maintaining high traction coefficient even upon high-temperature operation while keeping the formation of a traction oil film as carried out in the toroidal-type CVT in the earlier technique, and capable of transmitting a large driving force without increasing the pressing force to be applied to the rolling elements of the toroidal-type CVT.
  • CVT continuously variable transmission
  • the rolling elements have the traction surfaces having a surface microstructure defined with respect to a thickness of the traction oil film formed under the operating condition that the temperature of a traction portion of each traction surface is relatively high.
  • the toroidal-type CVT of the present invention therefore, can serve for maintaining rolling-fatigue lives of the rolling elements as kept in the rolling elements of the toroidal-type CVT in the earlier technique.
  • the toroidal-type CVT of the present invention also can serve for reducing the pressing force, so that the components of the CVT can be prevented from the increase in weight that is caused due to increase in the pressing force. Further, the toroidal-type CVT of the present invention can contribute to suppression of friction loss at bearings supporting the components to thereby reduce loss of automobile power.
  • a toroidal-type continuously variable transmission for automobiles comprising:
  • a toroidal-type continuously variable transmission for automobiles comprising:
  • a toroidal-type continuously variable transmission for automobiles comprising:
  • a toroidal-type continuously variable transmission for automobiles comprising:
  • Fig. 5 illustrates two-cylinder rolling tester 10 for carrying out rolling and sliding contact between two rolling elements T1 and T2 as test pieces.
  • two-cylinder rolling tester 10 includes primary shaft 11 that supports rolling element T1, and subsidiary shaft 12 that supports rolling element T2.
  • Torque sensor 13 is provided on primary shaft 11.
  • Primary shaft timing belt 15 is spanned on primary shaft 11 and motor shaft 14a of servo motor 14.
  • Subsidiary shaft 12 is rotatably supported by bearing 16 fixed on sliding base B. Sliding base B is movable in a direction perpendicular to the axial direction of subsidiary shaft 12.
  • Subsidiary shaft 12 is connected with motor shaft 17a of servo motor 17 fixed on sliding base B, through subsidiary shaft timing belt 18 spanned on subsidiary shaft 12 and motor shaft 17a.
  • Rolling element T2 supported on subsidiary shaft 12 is moved together with sliding base B and servo motor 17 by pressing sliding base B in the direction indicated by arrow of Fig. 5, with air cylinder 19. Rolling elements T1 and T2 thus come into rolling contact with each other in oil bath 20. Traction coefficient is calculated by measuring the torque generated at primary shaft 11 by torque sensor 13 provided on primary shaft 11 of the power transmission system on the rolling element T1 side.
  • Rolling element T1 was made of SCM420H steel (chromium molybdenum steel prescribed in JIS G 4052) subjected to carburizing-quenching-tempering, and formed by grinding and super finishing to a generally cylindrical shape having a diameter of 40 mm, a thickness of 20 mm and a crowning-shaped traction surface having R (radius) of 700 mm.
  • the microstructure of the traction surface had arithmetical mean roughness Ra of 0.021 ⁇ m, root-mean-square roughness Rq of 0.03 ⁇ m, oil retention volume Vo of 1.8x10 -6 mm 3 /mm 2 , and oil retention depth ratio K of 0.54.
  • the microstructure of the traction surface was measured using a tracer type surface roughness tester at a cutoff of 0.08 mm and a measuring length of 0.4 mm.
  • Rolling elements T2 were prepared.
  • Rolling elements T2 were made of SCM420H steel subjected to carburizing-quenching-tempering, and formed by various working processes to cylindrical shapes having a diameter of 40 mm, a thickness of 20 mm and cylindrical traction surfaces having different microstructures.
  • the microstructure of the traction surface of rolling element T2 was measured in the same manner as described above with respect to rolling element T1.
  • a set of thus-produced rolling element T1 and each of rolling elements T2 were installed in two-cylinder rolling tester 10 shown in Fig. 5, and the rolling and sliding test was conducted to measure the traction generated at the traction surfaces of rolling elements T1 and T2 and a rate of formation of the traction oil film formed therebetween.
  • Conditions of the rolling and sliding test using two-cylinder rolling tester 10 was as follows.
  • the slide/roll ratio was 0-5%.
  • the mean rolling velocity was 0.52-5.2 m/s.
  • the mean shaft rotation number was 250-2500 rpm (the arithmetical mean of the rotation numbers of primary shaft 11 and subsidiary shaft 12).
  • the mean rolling velocity was made constant by uniformly applying a differential to primary shaft 11 and subsidiary shaft 12.
  • the traction oil in oil bath 20 was set at 100°C.
  • the vertical load generated by the pressure applied by air cylinder 19 was set at 147 N.
  • the traction oil film formation rate was determined as a parameter of metal-to-metal contact of the traction surfaces of rolling elements T1 and T2 during the operation.
  • the metal-to-metal contact state of the traction surfaces of rolling elements T1 and T2 were monitored by electric resistance method during the rolling and sliding test.
  • the traction oil film formation rate is defined as a ratio of electric potential difference between the traction surfaces which was measured at the metal contact state, to electric potential difference therebetween when there was no metal-to-metal contact, was obtained.
  • Fig. 6 shows a relationship between traction stress ⁇ obtained from the results of the rolling and sliding test, and traction oil film thickness ratio ⁇ of traction oil film thickness h to surface roughness Rqsyn.
  • Traction stress ⁇ is the value obtained by dividing a traction force by an area of the traction portion of the traction surface.
  • ⁇ shows the traction surfaces formed with dimples in Example 1 and ⁇ shows those subjected to superfinishing in Example 2. Traction stress ⁇ becomes better in the direction indicated by the arrow of Fig. 6.
  • the equation of Hamrock and Dowson determines the relationship between dimensionless parameter and oil film thickness on the basis of an elastohydrodynamic lubrication (EHL) theory.
  • the EHL theory is at present a most accurate method of calculating an actual oil film thickness.
  • the EHL theory is based on the pressure-dependency of elastic deformation and lubricating oil viscosity of lubricated surfaces or parts.
  • the EHL theory gives generated pressure and lubricated surface configuration as a solution by simultaneously using Reynolds equation, the formula expressing a relationship between stress and strain on the lubricated surface (a relationship between pressure and lubricated surface deformation), and the formula expressing a relationship between pressure and lubricating oil viscosity.
  • Fig. 7 shows a relationship between a traction oil film formation rate and traction oil film thickness ratio ⁇ .
  • the traction oil film formation rate becomes better in the direction indicated by the arrow. It has been found that the traction oil film formation rate is affected by the configuration of surface roughness of the traction surfaces.
  • Fig. 8 shows groups A to D into which the microstructure of the traction surfaces are classified based on oil retention volume Vo and oil retention depth ratio K.
  • Group A includes the microstructure having oil retention depth ratio K of not less than 0.9 and oil retention volume Vo of not less than 7x10 -6 mm 3 /mm 2 .
  • the microstructure having oil retention depth ratio K of less than 0.9 are classified into groups D, B and C on the basis of oil retention volume Vo such that the value of oil retention volume Vo is decreased in this order.
  • the microstructure of group A has the relatively larger oil retention volume Vo as well as the larger oil retention depth ratio K as compared with those of the other groups. This indicates that if oil retention volume Vo is large, an absolute value of the valley depth of the surface roughness will be large.
  • Fig. 9 shows a relationship between traction coefficient and the traction oil film formation rate, which is expressed by groups A-D corresponding to those of Fig. 8. It has been recognized that group A exhibits the large traction coefficient and the high rate of traction oil film formation, as compared with groups B-D. That is, if the traction surface has the microstructure of group A, the high rate of traction oil film formation can be kept even when the traction oil film thickness is small, namely, the traction coefficient is large.
  • the microstructure of the traction surface is formed so as to have oil retention depth ratio K of not less than 0.9 and oil retention volume Vo of not less than 7x10 -6 mm 3 /mm 2 as exhibited in group A, the high rate of traction oil film formation can be kept with the large traction coefficient.
  • traction oil film thickness ratio ⁇ (h/Rqsyn) and traction stress ⁇ as shown in Fig. 6 will be given by the following reason. If traction oil film thickness ratio ⁇ becomes small, metal-to-metal contact or boundary friction larger than fluid friction will occur on tip ends of peaks of the surface roughness, causing a large apparent traction.
  • the rolling elements have the traction surfaces having the microstructure discussed above, so that metal-to-metal contact of the traction surfaces can be suppressed and the traction coefficient can be improved even at high temperature.
  • Fig. 10 shows a relationship between root-mean-square roughness value Rq ( ⁇ m) and oil retention volume Vo (mm 3 /mm 2 ), in which a magnitude of oil retention depth ratio K is indicated in proportion to a size of a plot.
  • a magnitude of oil retention depth ratio K is indicated in proportion to a size of a plot.
  • oil retention depth ratio K is not less than 0.9, the traction oil film formation rate can be kept high even when traction oil film thickness h becomes small. Further, if ratio h/Vosyn is not more than 15.0, traction stress ⁇ and the traction coefficient will increase. Namely, in a case where the microstructure of the traction surfaces is constructed such that ratio h/Vosyn is not more than 15.0 under the operating condition that the temperature of the traction portion of each traction surface is highest, the traction coefficient can increase even at the high temperature of the traction portions.
  • the microstructure of the traction surfaces is constructed such that oil retention depth ratio K is not less than 0.9, the high rate of traction oil film formation can be kept even when the traction oil film thickness becomes small. This can serve for suppressing the occurrence of metal-to-metal contact and maintaining substantially the same rolling-fatigue lives of the rolling elements of the toroidal-type CVT as those of the rolling elements of the toroidal-type CVT in the earlier technique. These effects can also be exhibited if the microstructure of the traction surfaces is constructed such that traction oil film thickness ratio A (h/Rqsyn) is not more than 3.
  • traction oil film thickness ratio A (h/Rqsyn) when traction oil film thickness ratio A (h/Rqsyn) is not more than 1, the traction coefficient as well as traction stress ⁇ becomes larger (see Fig. 6). This can exhibit more preferable effects. Furthermore, if traction oil film thickness ratio A (h/Rqsyn) is in a range of 0.2-1.0, the traction coefficient can be improved and metal-to-metal contact can be prevented. This can provide a traction drive excellent in durability. In addition, it has been found from the relationship shown in Fig. 10 that if oil retention depth ratio K is not less than 0.9, traction oil film thickness ratio A (h/Rqsyn) of 1.0 or less is equivalent to ratio h/Vosyn of 5.0 or less. Therefore, if the microstructure of the traction surfaces is constructed such that traction oil film thickness ratio h/Vosyn is not more than 5.0, the effects can be exhibited at maximum.
  • the traction oil film thickness formed at high temperature in the toroidal-type CVT for automobiles will be about 0.2 ⁇ m upon taking account of the allowable bearing pressure and heat resistance of materials of the traction surfaces, the revolution number and output limit of the engine, and the like. Therefore, if traction oil film thickness h is 0.2 ⁇ m as a constant value and traction oil film thickness ratio A (h/Rqsyn) is not more than 3.0, surface roughness Rqsyn can be not less than 0.07 ⁇ m. If traction oil film thickness h is 0.2 ⁇ m and ratio h/Vosyn is not more than 15.0, root-sum-square value Vosyn can be 1.3x10 -5 mm 3 /mm 2 .
  • traction oil film thickness h is 0.2 ⁇ m and traction oil film thickness ratio A (h/Rqsyn) is not more than 1.0
  • surface roughness Rqsyn can be not less than 0.2 ⁇ m.
  • traction oil film thickness h is 0.2 ⁇ m and traction oil film thickness ratio A (h/Rqsyn) is not less than 0.2
  • surface roughness Rqsyn can be not more than 1.0 ⁇ m.
  • root-sum-square value Vosyn can be 4x10 -5 mm 3 /mm 2 .
  • the microstructure of the traction surfaces of the rolling elements is constructed such that traction oil film thickness ratio h/Rqsyn is not more than 3.0 when oil retention depth ratio K of at least one of the traction surfaces is not less than 0.9 and oil retention volume Vo of the at least one of the traction surfaces is not less than 7x10 -6 mm 3 /mm 2 , where h is a thickness ( ⁇ m) of the traction oil film formed under the operating condition that a temperature of a traction portion of each traction surface is highest, and Rqsyn is a root-sum-square value of root-mean-square roughness values Rq ( ⁇ m) of the traction surfaces.
  • the toroidal-type CVT of the invention can suppress metal-to-metal contact of the traction surfaces, serving for maintaining substantially the same rolling-fatigue lives of the rolling elements of the toroidal-type as those of the rolling elements of the toroidal-type CVT in the earlier technique.
  • the toroidal-type CVT of the invention can also keep high traction coefficient even upon high-temperature operation of the CVT, serving for transmitting a large driving force without increasing the pressing force to be applied to the traction portions of the traction surfaces.
  • traction oil film thickness ratio h/Rqsyn may be not more than 1.0. In this case, the toroidal-type CVT of the invention can more stably exhibit the effects described above.
  • traction oil film thickness ratio h/Rqsyn may be in a range of 0.2-1.0, so that traction coefficient can be improved and metal-to-metal contact of the traction surfaces can be suppressed.
  • the toroidal-type CVT of the invention therefore, can be increased in durability.
  • the microstructure of the traction surfaces of the rolling elements is constructed such that oil retention depth ratio K of at least one of the traction surfaces is not less than 0.9 and ratio h/Vosyn is not more than 15.0, where h is a thickness (mm) of the traction oil film formed under the operating condition that a temperature of a traction portion of each traction surface is highest, and Vosyn is a root-sum-square value of oil retention volumes Vo (mm 3 /mm 2 ) of the traction surfaces.
  • Ratio h/Vosyn of not more than 15.0 corresponds to traction oil film thickness ratio h/Rqsyn of not more than 3.0, whereby the same effects as described above in the former case can be exhibited in the latter case. Further, ratio h/Vosyn may be not more than 5.0. This corresponds to traction oil film thickness ratio h/Rqsyn of not more than 1.0, whereby there can be more stably exhibited the same effects as in the case of traction oil film thickness ratio h/Rqsyn of not more than 1.0.
  • thickness h of the traction oil film is calculated on the basis of dimension and material characteristics of the traction surfaces, temperature condition, operating condition of the continuously variable transmission, and viscosity characteristics of the traction oil according to the EHL theory. Further, thickness h of the traction oil film is calculated using the equation of Hamrock and Dowson. Furthermore, the operating condition is the condition that an engine output is maximum and a temperature of a traction oil to be supplied to the traction surfaces is highest. The actual thickness of the traction oil film, therefore, can be calculated with remarkably high accuracy.
  • the microstructure of the traction surfaces of the rolling elements is constructed such that oil retention depth ratio K of at least one of the traction surfaces is not less than 0.9, oil retention volume Vo of the at least one of the traction surfaces is not less than 7x10 -6 mm 3 /mm 2 , and root-sum-square value Rqsyn of root-mean-square roughness values Rq of the traction surfaces is not less than 0.07 ⁇ m. If traction oil film thickness h is 0.2 ⁇ m as a constant value and root-sum-square value Rqsyn is not less than 0.07 ⁇ m, traction oil film thickness ratio h/Rqsyn can be not more than 3.0.
  • Root-sum-square value Rqsyn may be not less than 0.2 ⁇ m. If traction oil film thickness h is the constant value and root-sum-square value Rqsyn is not less than 0.2 ⁇ m, traction oil film thickness ratio h/Rqsyn can be not more than 1.0. The toroidal-type CVT of the invention can, therefore, more stably exhibit the effects as described in the case of traction oil film thickness ratio h/Rqsyn of not more than 1.0. Root-sum-square value Rqsyn may be in a range of 0.2-1.0 ⁇ m. If traction oil film thickness h is the constant value and root-sum-square value Rqsyn is in the range of 0.2-1.0 ⁇ m, traction oil film thickness ratio h/Rqsyn can be not more than 1.0.
  • the microstructure of the traction surfaces of the rolling elements is constructed such that oil retention depth ratio K of at least one of the traction surfaces is not less than 0.9, and root-sum-square value Vosyn of oil retention volumes Vo of the traction surfaces is not less than 1.3x10 -5 mm 3 /mm 2 . If traction oil film thickness h is 0.2 ⁇ m, i.e., 2x10 -4 mm, as a constant value and root-sum-square value Vosyn is not less than 1.3x10 -5 mm 3 /mm 2 , ratio h/Vosyn can be not more than 15.0.
  • Root-sum-square value Vosyn may be not less than 4x10 -5 mm 3 /mm 2 . If traction oil film thickness h is the constant value and root-sum-square value Vosyn is not less than 4x10 -5 mm 3 /mm 2 , ratio h/Vosyn can be not more than 5.0.
  • the toroidal-type CVT of the invention can, therefore, more stably exhibit the effects as described in the case of ratio h/Vosyn of not more than 5.0 and then in the case of traction oil film thickness ratio h/Rqsyn of not more than 1.0.
  • Example 1 (dimple-formed traction surface)
  • Rolling elements of the toroidal-type CVT of the invention were prepared corresponding to input disk 3, output disk 5 and power rollers 6 shown in Fig. 1.
  • the rolling elements were produced in the following manner.
  • Workpieces made of SCM420H steel (chromium molybdenum steel prescribed by JIS G 4052) were subjected to carburizing-quenching-tempering and then to grinding, superfinishing and shot peening to be formed with traction surfaces.
  • the shot peening was conducted by a pneumatic shot-peening machine at air pressure of 0.49 MPa (5 kg/cm 2 ) and using steel balls having Vickers hardness of Hv750 and mean particle diameter of 0.05 mm.
  • the projector nozzle was oscillated in a direction of the axis of rotation of each workpiece while rotating the workpiece, so that an amount of ball-projection was substantially uniform over the entire surface to be formed as the traction surface.
  • the ball-projection time was set at 20 sec. Random recesses and projections were formed in the surface by the shot peening. After the shot peening, the projections were cut away by tape lapping to thereby form dimples in the surface.
  • the rolling elements having the traction surfaces were thus produced.
  • a microstructure of the traction surface of each rolling elements was measured using a tracer type surface roughness tester to thereby calculate oil retention depth ratio K and oil retention volume Vo and root-mean-square roughness Rq. Results of the measurement are shown in Table 2.
  • a toroidal-type CVT as shown in Fig. 1 was assembled using thus-produced rolling elements.
  • the assembled toroidal-type CVT was operated to evaluate traction coefficient as traction performance under such a condition that a temperature of the traction portion of each traction surface was highest.
  • the operating condition was that an engine output was maximum, traction oil in an oil pan was about 120°C due to high environmental temperature, and change gear ratio was 1:1 at which the maximum heat was generated on the traction surfaces.
  • the evaluation results are shown in Table 2.
  • the temperature of the traction portion of each traction surface was approx. 150°C at maximum.
  • the viscosity characteristics of the traction oil, the pressing force that is applied to the traction surface at the maximum engine output and at the change gear ratio 1:1, and the rolling speed and equivalent curvature of the traction surface are given as follows on the basis of the dimension of the CVT, and the equivalent elastic coefficient of the traction surface is given as follows on the basis of properties of the components:
  • Thus-obtained traction oil film thickness h was 0.2 ⁇ m, i.e., 2x10 -4 mm.
  • Rolling elements were produced in the same manner as described in Example 1. Oil retention depth ratio K, oil retention volume Vo and root-mean-square roughness Rq of the traction surfaces of thus-produced rolling elements were calculated in the same manner as described in Example 1. The calculation results are shown in Table 2. A toroidal-type CVT as shown in Fig. 1 was assembled using the rolling elements and operated to evaluate the traction coefficient under the same condition as described in Example 1. The evaluation results are shown in Table 2.
  • Rolling elements were produced in the same manner as described in Example 1, except that, after grinding, the workpieces were subjected to ultra-precision cutting using a sintered cubic boron nitride (c-BN) tool having a round end of R (radius) of 50 ⁇ m under conditions that the cutting speed was 250 m/min, the feeding speed was 0.05 mm/rev, and the cutting depth in the radial direction was 0.02 mm. Subsequently, the projections of the surface of the workpieces were cut away by tape lapping. At this time, the tape lapping time for the respective surfaces of the workpieces was changed to adjust the machining allowance, so that grooves different in depth were formed in the surfaces, respectively.
  • c-BN sintered cubic boron nitride
  • the rolling elements were produced which had traction surfaces having the microstructure of a combination of a continuous circumferential groove and top-flat lands.
  • Oil retention depth ratio K and oil retention volume Vo and root-mean-square roughness Rq of the traction surfaces of thus-produced rolling elements were calculated in the same manner as described in Example 1. The calculation results are shown in Table 2.
  • a toroidal-type CVT as shown in Fig. 1 was assembled using the rolling elements and operated to evaluate the traction coefficient under the same condition as described in Example 1. The evaluation results are shown in Table 2.
  • Rolling elements were produced in the same manner as described in Example 1 except that the grinding and superfinishing were conducted such that root-mean-square roughness values Rq were indicated as shown in Table 2.
  • Oil retention depth ratio K and oil retention volume Vo and root-mean-square roughness Rq of the traction surfaces of thus-produced rolling elements were calculated in the same manner as described in Example 1. The calculation results are shown in Table 2.
  • a toroidal-type CVT as shown in Fig. 1 was assembled using the rolling elements and operated to evaluate the traction coefficient under the same condition as described in Example 1. The evaluation results are shown in Table 2.
  • Rolling elements were produced in the same manner as described in Examples 3 and 4, except that the groove formed in the traction surface of each rolling element was deeper than those of Examples 3 and 4.
  • Oil retention depth ratio K and oil retention volume Vo and root-mean-square roughness Rq of the traction surfaces of thus-produced rolling elements were calculated in the same manner as described in Example 1. The calculation results are shown in Table 2.
  • a toroidal-type CVT as shown in Fig. 1 was assembled using the rolling elements and operated to evaluate the traction coefficient under the same condition as described in Example 1. The evaluation results are shown in Table 2.
  • Example 1 As be apparent from the results shown in Table 2, excellent traction performance was exhibited in Example 1 as compared with Comparative Examples 1 and 2.
  • ratio h/Rqsyn of traction oil film thickness h ( ⁇ m) to root-sum-square value Rqsyn of root-mean-square roughness values Rq of the traction surfaces was not more than 3.0 when oil retention depth ratio K was not less than 0.9 and oil retention volume Vo was not less than 7x10 -6 mm 3 /mm 2 under the operating condition that the temperature of the traction portion of each traction surface was highest.
  • Example 1 ratio h/Vosyn of traction oil film thickness h (mm) to root-sum-square value of oil retention volumes Vo (mm 3 /mm 2 ) of the traction surfaces was not more than 15.0 when oil retention depth ratio K was not less than 0.9 under the operating condition that the temperature of the traction portion of each traction surface was highest. In Examples 2 and 3, more excellent traction coefficients were exhibited. In contrast, in Comparative Examples 1 and 2, satisfactory traction coefficient was not exhibited. In Comparative Example 2, root-sum-square value Rqsyn was not less than 1.0 ⁇ m and ratio h/Rqsyn was not more than 0.2. This caused vibration of the rolling elements to increase during the evaluation test, so that the evaluation test was interrupted. The traction surfaces had peelings as well as fine cracks when observed. It has been found that the rolling elements were poor in durability in Comparative Example 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • General Details Of Gearings (AREA)

Claims (13)

  1. Transmission à variation continue toroïdale pour automobiles, comprenant :
    une pluralité d'éléments de roulement présentant des surfaces de traction coopérant les unes avec les autres pour transmettre une puissance entre les éléments de roulement par l'intermédiaire d'un film d'huile de traction formé entre les surfaces de traction,
       caractérisée en ce qu'un rapport h/Rqsyn n'est pas supérieur à 3,0 lorsqu'un rapport de profondeur de rétention d'huile K d'au moins l'une des surfaces de traction n'est pas inférieur à 0,9, et un volume de rétention d'huile Vo de ladite au moins une des surfaces de traction n'est pas inférieur à 7x10-6 mm3/mm2, où
       h est une épaisseur du film d'huile de traction formé à l'état de fonctionnement,
       Rq correspond aux valeurs de rugosité moyennes quadratiques des surfaces de traction, et
       Rqsyn est une valeur résultante quadratique des valeurs de rugosité moyennes quadratiques des surfaces de traction.
  2. Transmission à variation continue toroïdale selon la revendication 1, dans laquelle le rapport h/Rqsyn n'est pas supérieur à 1,0.
  3. Transmission à variation continue toroïdale selon la revendication 1, dans laquelle le rapport h/Rqsyn se situe dans une plage de 0,2 à 1,0.
  4. Transmission à variation continue toroïdale pour automobiles, comprenant :
    une pluralité d'éléments de roulement présentant des surfaces de traction coopérant les unes avec les autres pour transmettre une puissance entre les éléments de roulement par l'intermédiaire d'un film d'huile de traction formé entre les surfaces de traction,
       caractérisée en ce qu'un rapport de profondeur de rétention d'huile K d'au moins l'une des surfaces de traction n'est pas inférieur à 0,9, et un rapport h/Vosyn n'est pas supérieur à 15,0, où
       h est une épaisseur du film d'huile de traction formé à l'état de fonctionnement,
       Vo correspond aux volumes de rétention d'huile des surfaces de traction, et
       Vosyn est une valeur résultante quadratique des volumes de rétention d'huile des surfaces de traction.
  5. Transmission à variation continue toroïdale selon la revendication 4, dans laquelle le rapport h/Vosyn n'est pas supérieur à 5,0.
  6. Transmission à variation continue toroïdale selon l'une quelconque des revendications 1 à 4, dans laquelle l'épaisseur h du film d'huile de traction est calculée sur la base de caractéristiques dimensionnelles et matérielles des surfaces de traction, de l'état thermique, de l'état de fonctionnement de la transmission à variation continue, et de caractéristiques de viscosité de l'huile de traction selon une théorie de lubrification élasto-hydrodynamique.
  7. Transmission à variation continue toroïdale selon la revendication 6, dans laquelle l'épaisseur h du film d'huile de traction est calculée en utilisant l'équation de Hamrock et Dowson : H = 3,42gv0,49gE0,17(1-e-0,68k) où H = (h/Rx) (W/U) gv = GW3/U2 gE = W8/3/U2 k = (Ry/Rx)2/x U = ηou/(E'Rx) W = w/(E'Rx2) G = αE' où
       H est un paramètre d'une épaisseur de film, gv est un paramètre de viscosité, gE est un paramètre d'élasticité, et k est un paramètre d'ellipse, Rx est un rayon de courbure équivalent dans une direction de roulement de la partie de traction de la surface de traction, W est un paramètre de charge, U est un paramètre de vitesse, G est un paramètre de matériau, Ry est un rayon de courbure équivalent dans une direction perpendiculaire à la direction de roulement de la partie de traction de la surface de traction, ηo est une viscosité d'huile sous pression atmosphérique, u est une vitesse de roulement de la partie de traction de la surface de traction, E' est un coefficient élastique vertical équivalent de la partie de traction de la surface de traction, w est une force de pressage appliquée à la partie de traction de la surface de traction, et α est un coefficient viscosité-pression.
  8. Transmission à variation continue toroïdale selon l'une quelconque des revendications 1 à 7, dans laquelle l'état de fonctionnement est l'état dans lequel un rendement du moteur est maximal et une température d'une huile de traction à fournir aux surfaces de traction est la plus haute.
  9. Transmission à variation continue toroïdale pour automobiles, comprenant :
    une pluralité d'éléments de roulement présentant des surfaces de traction coopérant les unes avec les autres pour transmettre une puissance entre les éléments de roulement par l'intermédiaire d'un film d'huile de traction formé entre les surfaces de traction,
       caractérisée en ce qu'un rapport de profondeur de rétention d'huile K d'au moins l'une des surfaces de traction n'est pas inférieur à 0,9, un volume de rétention d'huile Vo de ladite au moins une des surfaces de traction n'est pas inférieur à 7x10-6 mm3/mm2, et une valeur résultante quadratique Rqsyn des valeurs de rugosité moyennes quadratiques Rq des surfaces de traction n'est pas inférieure à 0,07 µm.
  10. Transmission à variation continue toroïdale selon la revendication 9, dans laquelle la valeur résultante quadratique Rqsyn n'est pas inférieure à 0,2 µm.
  11. Transmission à variation continue toroïdale selon la revendication 9, dans laquelle la valeur résultante quadratique Rqsyn se situe dans une plage de 0,2 à 1,0 µm.
  12. Transmission à variation continue toroïdale pour automobiles, comprenant :
    une pluralité d'éléments de roulement présentant des surfaces de traction coopérant les unes avec les autres pour transmettre une puissance entre les éléments de roulement par l'intermédiaire d'un film d'huile de traction formé entre les surfaces de traction,
       caractérisée en ce qu'un rapport de profondeur de rétention d'huile K d'au moins l'une des surfaces de traction n'est pas inférieur à 0,9 et une valeur résultante quadratique Vosyn des volumes de rétention d'huile Vo des surfaces de traction n'est pas inférieure à 1,3x10-5 mm3/mm2.
  13. Transmission à variation continue toroïdale selon la revendication 12, dans laquelle la valeur résultante quadratique Vosyn n'est pas inférieure à 4x10-5 mm3/mm2.
EP01106700A 2000-03-23 2001-03-16 Transmission continue du type torique pour véhicules Expired - Lifetime EP1136724B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000081587 2000-03-23
JP2000081587A JP3630297B2 (ja) 2000-03-23 2000-03-23 自動車用トロイダル式無段変速機

Publications (3)

Publication Number Publication Date
EP1136724A2 EP1136724A2 (fr) 2001-09-26
EP1136724A3 EP1136724A3 (fr) 2004-01-21
EP1136724B1 true EP1136724B1 (fr) 2005-08-17

Family

ID=18598504

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01106700A Expired - Lifetime EP1136724B1 (fr) 2000-03-23 2001-03-16 Transmission continue du type torique pour véhicules

Country Status (4)

Country Link
US (1) US6524212B2 (fr)
EP (1) EP1136724B1 (fr)
JP (1) JP3630297B2 (fr)
DE (1) DE60112638T2 (fr)

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7651437B2 (en) 2003-02-28 2010-01-26 Fallbrook Technologies Inc. Continuously variable transmission
US7654928B2 (en) 2003-08-11 2010-02-02 Fallbrook Technologies Inc. Continuously variable planetary gear set
US7670243B2 (en) 2005-08-24 2010-03-02 Fallbrook Technologies, Inc. Continuously variable transmission
US7727101B2 (en) 2005-10-28 2010-06-01 Fallbrook Technologies Inc. Electromotive drives
US7727107B2 (en) 1997-09-02 2010-06-01 Fallbrook Technologies Inc. Continuously variable transmission
US7762919B2 (en) 2004-10-05 2010-07-27 Fallbrook Technologies Inc. Continuously variable transmission
US7871353B2 (en) 2005-12-09 2011-01-18 Fallbrook Technologies Inc. Continuously variable transmission
US7883442B2 (en) 2001-04-26 2011-02-08 Fallbrook Technologies Inc. Continuously variable transmission
US7914029B2 (en) 2005-11-22 2011-03-29 Fallbrook Technologies Inc. Continuously variable transmission
US8087482B2 (en) 2006-03-14 2012-01-03 Fallbrook Technologies Inc. Wheelchair
US8167759B2 (en) 2008-10-14 2012-05-01 Fallbrook Technologies Inc. Continuously variable transmission
US8313404B2 (en) 2007-02-16 2012-11-20 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8313405B2 (en) 2008-02-29 2012-11-20 Fallbrook Intellectual Property Company Llc Continuously and/or infinitely variable transmissions and methods therefor
US8317651B2 (en) 2008-05-07 2012-11-27 Fallbrook Intellectual Property Company Llc Assemblies and methods for clamping force generation
US8321097B2 (en) 2007-12-21 2012-11-27 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US8360917B2 (en) 2009-04-16 2013-01-29 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8376903B2 (en) 2006-11-08 2013-02-19 Fallbrook Intellectual Property Company Llc Clamping force generator
US8393989B2 (en) 2007-04-24 2013-03-12 Fallbrook Intellectual Property Company Llc Electric traction drives
US8398518B2 (en) 2008-06-23 2013-03-19 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8480529B2 (en) 2006-06-26 2013-07-09 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8506452B2 (en) 2005-12-30 2013-08-13 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8512195B2 (en) 2010-03-03 2013-08-20 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8535199B2 (en) 2008-06-06 2013-09-17 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8641577B2 (en) 2007-06-11 2014-02-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8738255B2 (en) 2007-02-01 2014-05-27 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US8776633B2 (en) 2006-01-30 2014-07-15 Fallbrook Intellectual Property Company Llc System for manipulating a continuously variable transmission
US8818661B2 (en) 2008-08-05 2014-08-26 Fallbrook Intellectual Property Company Llc Methods for control of transmission and prime mover
US8845485B2 (en) 2011-04-04 2014-09-30 Fallbrook Intellectual Property Company Llc Auxiliary power unit having a continuously variable transmission
US8888643B2 (en) 2010-11-10 2014-11-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8900085B2 (en) 2007-07-05 2014-12-02 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8996263B2 (en) 2007-11-16 2015-03-31 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US9371894B2 (en) 2007-02-12 2016-06-21 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE41892E1 (en) 1997-09-02 2010-10-26 Fallbrook Technologies Inc. Continuously variable transmission
JP3555844B2 (ja) * 1999-04-09 2004-08-18 三宅 正二郎 摺動部材およびその製造方法
JP3664058B2 (ja) * 1999-09-07 2005-06-22 日産自動車株式会社 トラクションドライブ用転動体およびその製造方法
JP3736619B2 (ja) * 2000-06-29 2006-01-18 日産自動車株式会社 トロイダル型無段変速機
JP2003184883A (ja) 2001-12-20 2003-07-03 Nissan Motor Co Ltd 軸受摺動部材
JP3555891B2 (ja) * 2002-02-22 2004-08-18 新日本石油株式会社 低摩擦摺動材料及びこれに用いる潤滑油組成物
ES2402127T3 (es) * 2002-09-30 2013-04-29 Rohs, Ulrich Transmisión con anillo cónico de fricción
JP4988198B2 (ja) 2002-09-30 2012-08-01 ロース，ウルリヒ 回転変速機
ES2431114T3 (es) 2002-09-30 2013-11-25 Ulrich Rohs Transmisión
US6969198B2 (en) * 2002-11-06 2005-11-29 Nissan Motor Co., Ltd. Low-friction sliding mechanism
JP3891433B2 (ja) * 2003-04-15 2007-03-14 日産自動車株式会社 燃料噴射弁
EP1479946B1 (fr) * 2003-05-23 2012-12-19 Nissan Motor Co., Ltd. Piston pour un moteur à combustion interne
JP2005008851A (ja) * 2003-05-29 2005-01-13 Nissan Motor Co Ltd 硬質炭素薄膜付き機械加工工具用切削油及び硬質炭素薄膜付き機械加工工具
JP4863152B2 (ja) * 2003-07-31 2012-01-25 日産自動車株式会社 歯車
KR101003865B1 (ko) * 2003-08-06 2010-12-30 닛산 지도우샤 가부시키가이샤 저마찰 접동 기구, 저마찰제 조성물 및 마찰 감소 방법
JP4973971B2 (ja) * 2003-08-08 2012-07-11 日産自動車株式会社 摺動部材
JP4117553B2 (ja) * 2003-08-13 2008-07-16 日産自動車株式会社 チェーン駆動装置
US7771821B2 (en) * 2003-08-21 2010-08-10 Nissan Motor Co., Ltd. Low-friction sliding member and low-friction sliding mechanism using same
EP1508611B1 (fr) 2003-08-22 2019-04-17 Nissan Motor Co., Ltd. Boîte de vitesse comprenant une composition d`huile de transmission
US7878777B2 (en) * 2006-08-25 2011-02-01 Denso Corporation Scroll compressor having grooved thrust bearing
US8152687B2 (en) * 2007-01-24 2012-04-10 Torotrack (Development) Limited Powdered metal variator components
EP2441478B1 (fr) * 2008-04-17 2019-04-03 Dentsply IH AB Dispositif médical amélioré doté d'un revêtement hydrophile
AU2013212557C1 (en) 2012-01-23 2017-09-21 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
EP2986494A1 (fr) 2013-04-19 2016-02-24 Fallbrook Intellectual Property Company LLC Transmission à variation continue
JP6584054B2 (ja) * 2014-03-28 2019-10-02 住友重機械工業株式会社 偏心揺動型減速装置
US10047861B2 (en) 2016-01-15 2018-08-14 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
JP7137475B2 (ja) 2016-03-18 2022-09-14 フォールブルック インテレクチュアル プロパティー カンパニー エルエルシー 連続可変変速機、システムおよび方法
US10023266B2 (en) 2016-05-11 2018-07-17 Fallbrook Intellectual Property Company Llc Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmissions
US11215268B2 (en) 2018-11-06 2022-01-04 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same
US11174922B2 (en) 2019-02-26 2021-11-16 Fallbrook Intellectual Property Company Llc Reversible variable drives and systems and methods for control in forward and reverse directions
JP6885491B2 (ja) 2019-04-26 2021-06-16 日本精工株式会社 摺動部材の摩擦設計方法および表面粗さ管理方法並びに摺動機構の製造方法

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4909092A (en) * 1988-04-18 1990-03-20 Nippon Seiko Kabushiki Kaisha Toroidal type infinitely variable transmission
JPH05340456A (ja) * 1992-06-08 1993-12-21 Nippon Seiko Kk 動力伝達装置
US5372033A (en) 1993-11-18 1994-12-13 Mobil Oil Corporation EHL test machine for measuring lubricant film thickness and traction
JP2603559Y2 (ja) * 1993-12-07 2000-03-15 日本精工株式会社 トロイダル型無段変速機
JP3022111B2 (ja) 1993-12-17 2000-03-15 日産自動車株式会社 摩擦車式無段変速機の組立方法
JPH08296709A (ja) * 1995-04-26 1996-11-12 Nissan Motor Co Ltd 高面圧転動体
JP3385882B2 (ja) * 1996-11-19 2003-03-10 日産自動車株式会社 トロイダル型無段変速機の油圧制御装置
DE19829631B4 (de) * 1997-07-04 2006-01-19 Nsk Ltd. Stufenlos verstellbares Toroidgetriebe
JP3661371B2 (ja) * 1997-10-31 2005-06-15 日本精工株式会社 トロイダル形無段変速機のパワーローラ軸受
JP4101350B2 (ja) * 1997-11-10 2008-06-18 日本精工株式会社 トロイダル形無段変速装置
JP3407663B2 (ja) * 1998-07-30 2003-05-19 日産自動車株式会社 トロイダル型無段変速機の制御切換装置

Cited By (91)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7727107B2 (en) 1997-09-02 2010-06-01 Fallbrook Technologies Inc. Continuously variable transmission
US7837592B2 (en) 1997-09-02 2010-11-23 Fallbrook Technologies Inc. Continuously variable transmission
US7883442B2 (en) 2001-04-26 2011-02-08 Fallbrook Technologies Inc. Continuously variable transmission
US9046158B2 (en) 2003-02-28 2015-06-02 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US7727108B2 (en) 2003-02-28 2010-06-01 Fallbrook Technologies Inc. Continuously variable transmission
US7651437B2 (en) 2003-02-28 2010-01-26 Fallbrook Technologies Inc. Continuously variable transmission
US8469853B2 (en) 2003-02-28 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8628443B2 (en) 2003-02-28 2014-01-14 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8267829B2 (en) 2003-02-28 2012-09-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US7731615B2 (en) 2003-02-28 2010-06-08 Fallbrook Technologies Inc. Continuously variable transmission
US7686729B2 (en) 2003-02-28 2010-03-30 Fallbrook Technologies Inc. Continuously variable transmission
US8066614B2 (en) 2003-02-28 2011-11-29 Fallbrook Technologies, Inc. Continuously variable transmission
US7654928B2 (en) 2003-08-11 2010-02-02 Fallbrook Technologies Inc. Continuously variable planetary gear set
US7727110B2 (en) 2003-08-11 2010-06-01 Fallbrook Technologies Inc. Continuously variable planetary gear set
US7762920B2 (en) 2004-10-05 2010-07-27 Fallbrook Technologies Inc. Continuously variable transmission
US8123653B2 (en) 2004-10-05 2012-02-28 Fallbrook Technologies Inc. Continuously variable transmission
US8920285B2 (en) 2004-10-05 2014-12-30 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US7762919B2 (en) 2004-10-05 2010-07-27 Fallbrook Technologies Inc. Continuously variable transmission
US7963880B2 (en) 2004-10-05 2011-06-21 Fallbrook Technologies Inc. Continuously variable transmission
US7967719B2 (en) 2004-10-05 2011-06-28 Fallbrook Technologies Inc. Continuously variable transmission
US7976426B2 (en) 2004-10-05 2011-07-12 Fallbrook Technologies Inc. Continuously variable transmission
US8066613B2 (en) 2004-10-05 2011-11-29 Fallbrook Technologies Inc. Continuously variable transmission
US7909727B2 (en) 2004-10-05 2011-03-22 Fallbrook Technologies Inc. Continuously variable transmission
US8171636B2 (en) 2004-10-05 2012-05-08 Fallbrook Technologies Inc. Method of manufacturing a stator of a cage for a continuously variable transmission (CVT)
US8133149B2 (en) 2004-10-05 2012-03-13 Fallbrook Technologies Inc. Continuously variable transmission
US7670243B2 (en) 2005-08-24 2010-03-02 Fallbrook Technologies, Inc. Continuously variable transmission
US7828685B2 (en) 2005-10-28 2010-11-09 Fallbrook Technologies Inc. Electromotive drives
US7727101B2 (en) 2005-10-28 2010-06-01 Fallbrook Technologies Inc. Electromotive drives
US9506562B2 (en) 2005-10-28 2016-11-29 Fallbrook Intellectual Property Company Llc Electromotive drives
US8550949B2 (en) 2005-10-28 2013-10-08 Fallbrook Intellectual Property Company Llc Electromotive drives
US8342999B2 (en) 2005-10-28 2013-01-01 Fallbrook Intellectual Property Company Llc Electromotive drives
US8070635B2 (en) 2005-10-28 2011-12-06 Fallbrook Technologies Inc. Electromotive drives
US9022889B2 (en) 2005-10-28 2015-05-05 Fallbrook Intellectual Property Company Llc Electromotive drives
US9341246B2 (en) 2005-11-22 2016-05-17 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8708360B2 (en) 2005-11-22 2014-04-29 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US7914029B2 (en) 2005-11-22 2011-03-29 Fallbrook Technologies Inc. Continuously variable transmission
US7871353B2 (en) 2005-12-09 2011-01-18 Fallbrook Technologies Inc. Continuously variable transmission
US8317650B2 (en) 2005-12-09 2012-11-27 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9121464B2 (en) 2005-12-09 2015-09-01 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8262536B2 (en) 2005-12-09 2012-09-11 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US7959533B2 (en) 2005-12-09 2011-06-14 Fallbrook Technologies Inc. Continuously variable transmission
US8506452B2 (en) 2005-12-30 2013-08-13 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8776633B2 (en) 2006-01-30 2014-07-15 Fallbrook Intellectual Property Company Llc System for manipulating a continuously variable transmission
US8087482B2 (en) 2006-03-14 2012-01-03 Fallbrook Technologies Inc. Wheelchair
US8480529B2 (en) 2006-06-26 2013-07-09 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9017207B2 (en) 2006-06-26 2015-04-28 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9086145B2 (en) 2006-11-08 2015-07-21 Fallbrook Intellectual Property Company Llc Clamping force generator
US8376903B2 (en) 2006-11-08 2013-02-19 Fallbrook Intellectual Property Company Llc Clamping force generator
US8738255B2 (en) 2007-02-01 2014-05-27 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US9328807B2 (en) 2007-02-01 2016-05-03 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US9371894B2 (en) 2007-02-12 2016-06-21 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor
US8313404B2 (en) 2007-02-16 2012-11-20 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US9239099B2 (en) 2007-02-16 2016-01-19 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8585528B2 (en) 2007-02-16 2013-11-19 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US9273760B2 (en) 2007-04-24 2016-03-01 Fallbrook Intellectual Property Company Llc Electric traction drives
US8393989B2 (en) 2007-04-24 2013-03-12 Fallbrook Intellectual Property Company Llc Electric traction drives
US9574643B2 (en) 2007-04-24 2017-02-21 Fallbrook Intellectual Property Company Llc Electric traction drives
US8641577B2 (en) 2007-06-11 2014-02-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8900085B2 (en) 2007-07-05 2014-12-02 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8996263B2 (en) 2007-11-16 2015-03-31 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US9249880B2 (en) 2007-12-21 2016-02-02 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US8321097B2 (en) 2007-12-21 2012-11-27 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US8626409B2 (en) 2007-12-21 2014-01-07 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US8622866B2 (en) 2008-02-29 2014-01-07 Fallbrook Intellectual Property Company Llc Continuously and/or infinitely variable transmissions and methods therefor
US8313405B2 (en) 2008-02-29 2012-11-20 Fallbrook Intellectual Property Company Llc Continuously and/or infinitely variable transmissions and methods therefor
US9182018B2 (en) 2008-02-29 2015-11-10 Fallbrook Intellectual Property Company Llc Continuously and/or infinitely variable transmissions and methods therefor
US8317651B2 (en) 2008-05-07 2012-11-27 Fallbrook Intellectual Property Company Llc Assemblies and methods for clamping force generation
US8678974B2 (en) 2008-05-07 2014-03-25 Fallbrook Intellectual Property Company Llc Assemblies and methods for clamping force generation
US8535199B2 (en) 2008-06-06 2013-09-17 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8790214B2 (en) 2008-06-06 2014-07-29 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US9528561B2 (en) 2008-06-23 2016-12-27 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9074674B2 (en) 2008-06-23 2015-07-07 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8641572B2 (en) 2008-06-23 2014-02-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8398518B2 (en) 2008-06-23 2013-03-19 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8818661B2 (en) 2008-08-05 2014-08-26 Fallbrook Intellectual Property Company Llc Methods for control of transmission and prime mover
US9365203B2 (en) 2008-08-05 2016-06-14 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US8852050B2 (en) 2008-08-26 2014-10-07 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8469856B2 (en) 2008-08-26 2013-06-25 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8496554B2 (en) 2008-10-14 2013-07-30 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8870711B2 (en) 2008-10-14 2014-10-28 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9574642B2 (en) 2008-10-14 2017-02-21 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8167759B2 (en) 2008-10-14 2012-05-01 Fallbrook Technologies Inc. Continuously variable transmission
US9279482B2 (en) 2009-04-16 2016-03-08 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8360917B2 (en) 2009-04-16 2013-01-29 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8663050B2 (en) 2009-04-16 2014-03-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9360089B2 (en) 2010-03-03 2016-06-07 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8721485B2 (en) 2010-03-03 2014-05-13 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8512195B2 (en) 2010-03-03 2013-08-20 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US8888643B2 (en) 2010-11-10 2014-11-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9291251B2 (en) 2010-11-10 2016-03-22 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8845485B2 (en) 2011-04-04 2014-09-30 Fallbrook Intellectual Property Company Llc Auxiliary power unit having a continuously variable transmission

Also Published As

Publication number Publication date
EP1136724A3 (fr) 2004-01-21
EP1136724A2 (fr) 2001-09-26
US20020010051A1 (en) 2002-01-24
DE60112638D1 (de) 2005-09-22
JP2001263443A (ja) 2001-09-26
DE60112638T2 (de) 2006-06-14
US6524212B2 (en) 2003-02-25
JP3630297B2 (ja) 2005-03-16

Similar Documents

Publication Publication Date Title
EP1136724B1 (fr) Transmission continue du type torique pour véhicules
US6447168B2 (en) Tapered roller bearings and gear shaft support devices
US7958635B2 (en) Process for producing a pulley for a continuously variable belt drive transmission
KR100389247B1 (ko) 트랙션 구동 회전 조립체 및 이 조립체의 롤링 요소를 제조하는 방법
US7806793B2 (en) Continuously variable belt drive transmission
US8955225B2 (en) Method for producing an actuator
CN111919040B (zh) 锥形滚柱轴承
US20020051594A1 (en) Roller bearing
EP1219863A2 (fr) Eléments de roulement d'une de transmission à variation continue et son procédé de fabrication
US9850998B2 (en) Powered metal variator components
JP2023155324A (ja) 円すいころ軸受
JP7272767B2 (ja) 円錐ころ軸受
EP1235002B1 (fr) Ensemble rotatif d'un variateur de vitesse
JP7449059B2 (ja) 円すいころ軸受
JPH03277823A (ja) 等速自在継手
EP1770293B1 (fr) Roulement a rouleaux pour automobile
JP2019066038A (ja) 円錐ころ軸受
JP3685088B2 (ja) 自動車用トロイダル式無段変速機
JP7136627B2 (ja) 円すいころ軸受
JP7449058B2 (ja) 円すいころ軸受
JP2002243011A (ja) トラクションドライブ用転動体
JP7405544B2 (ja) 円すいころ軸受
Yamanaka et al. Performance of a low-spin disk for a shaft-drive continuously variable transmission
JPH08296709A (ja) 高面圧転動体

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20010316

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

AKX Designation fees paid

Designated state(s): DE FR GB

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 60112638

Country of ref document: DE

Date of ref document: 20050922

Kind code of ref document: P

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20060518

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20061130

REG Reference to a national code

Ref country code: FR

Ref legal event code: D3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060331

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20140311

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20140312

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140417

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 60112638

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20150316

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20151130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151001

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150316

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150331